dombrowski



Feb. 5, 1963 E. J. DOMBROWSKI 3, ,6

TRANSFER MECHANISM FOR CALCULATING MACHINES I Filed Feb. 21, 1962 4Sheets-Sheet 1 ATTOK/Vf) Feb. 5, 1963 E. J. DOMBROWSKI 3,

TRANSFER MECHANISM FOR CALCULATING MACHINES Filed Feb. 21, 1962 4Sheets-Sheet 2 INVENTOR. EDWARD J fidMbWOM JK/ Feb. 5, 1963 E. .1.DOMBROWSKI 3,

TRANSFER MECHANISM FOR CALCULATING MACHINES Filed Feb. 21, 1962 4Sheets-Sheet 3 INVEN TOR. [0/4 1450 J'- DflA/BAUWIK/ Feb. 5, 1963 J,DQMBROWSKI 3,076,602

TRANSFER MECHANISM FOR CALCULATING MACHINES Filed Feb. 21, 1962 4Sheets-Sheet 4 --\\m. V H4 10. H6? 72. Y I 37 im 35 I. :5 33= 190 1 3:

ATTORNEY United States Patent Ofiice 3,076,602 TRANSFER MECHANISM FORCALQULATING MACHXNES Edward J. Dombrowsld, Derby, Conn, assignor toSperry Rand Corporation, New York, N.Y., a corporation of Delaware FiledFeb. 21, 1962, Ser. No. 174,854

18 Claims. (Cl. 235-137) This invention relates to transfer mechanismsfor calculating machines and the like, and more particularly to suchmechanisms for effecting primary and secondary transfer operationssimultaneously with each other. Transfer mechanisms of the presentinvention may be usefully employed in various types of machines operablefor accumulating items, such as, machines for adding and/or subtracting,calculating, item registering, accounting, and bookkeeping, providedthat such machines utilize a mechanically operating memory device foreach denominational order for storing the items accumulated by themachine. Transfer mechanisms are provided in such machines fortransferring one unit to a memory device of a higher order eitheradditively or subtractively when the memory device of the next lowerorder accumulates its capacity and must therefore transfer itsaccumulation, as a unit, to the next higher order.

For example, in machines arranged for accumulating items in decimalnotation form by means of an accumulator or storage device for eachorder, Whenever the accumulator device of an order accumulates through 9to 0, or vice versa, as the case may be, its accumulation must betransferred, as a unit, to the accumulator device of the next higherorder, either additively or subtractively. Under conditions where such atransfer to a higher order accumulator device is directly initiated bythe entering of an item input into the accumulator device of its nextlower order, rather than by a transfer of a unit input into such nextlower order, it is termed a primary transfer operation.

- It maylhappen that the accumulator device into which the transfer unitis entered during the primary transfer operation is itself accumulatedto capacity, and is, thus, in turn, moved from 9 to 0, or vice versa,which movement may be termed through its transfer position, thuscausing, in turn, a unit transfer of its accumulation into theaccumulator device of the next, next higher order. This second transferoperation, which is directly initiated by a primary transfer and onlyindirectly by an item entering operation, may betermed a secondarytransfer. Such a secondary transfer may, in turn, initiate othersecondary transfers in successive next higher orders. Normally, suchadditional secondary transfers follow each other in aripple-likesequence, such that the cycling time of the machine must be lengthenedappreciably in order to allow for the total time required to perform thepossible maximum number of secondary transfers, which lengthening isundesirable. Since the amount of maximum secondary transfer time whichmust be allowed for increases in proportion to the number of orders forwhich the machine is equipped, such lengthening may become prohibitive,or, in any case economically unfeasible.

In attempts to minimize the cycling time of such calculating machines,transfer mechanisms for effecting primary and secondary transferoperations concurrently with each other have been devised. However, suchtransfer mechanisms, which may be termed simultaneous, usually requiredan additional time consuming conditioning or presensing operation of thetransfer actuator means before their operat'on, and are of intricatedesign, thereby tending to be uneconomical and unreliable.

Other transfer mechanisms of the simultaneous type undesirably are notsufiiciently positive acting, and, while 3,076,602 Patented Feb. 5, 1963tending to initiate primary and secondary transfer operationssimultaneously, do not effect their completion simultaneously; thelatter deficiency usually being due to operating tolerances necessarilyprovided between coacting parts of their respective mechanisms. Suchnecessary operating tolerances introduce a lag in the sequence ofsecondary transfer, which lag increase in magnitude in proport'on to thenumber of orders involved in the secondary transfer sequence and, incertain cases, is appreciable. This lag, in addition, may often be ofunpredictable varying magnitude and, if not, compensated for, results inmisalignment of the accumulator devices, particularly the ones towardsthe end of the transfer sequence. This, in turn, results in inaccuratestorage of input items by the calculator. Such transfer mechanisms,therefore, tend to be unreliable. In addition, wear and tear of thecoacting parts, of the calculator tend to increase the dimensions of theaforementioned operating tolerances, thereby causing the calculators, aswear continues, to become progressively less reliable.

Attempts have been made to improve the reliability of such calculatorsby devising and incorporating therein independently acting finalalignment devices which are effective after the operation of thetransfer mechanism to bring the accumulator devices into proper finalalignment. Such alignment devices, in effect, complete the transferoperations; However, they require additional control mechanism for theiroperation, undesirably in crease the cycling time of the machine, add toits manu facturfng cost, and make for a more intricate design which maymalfunction.

It is, therefore, an object of the invention to provide for calculatingmachines transfer mechanism whichis of simple construction, reliable,and effective to minimize the t'me consumed by transfer operations.

Another object is to provide in such machines transfer.

mechanism which effects all the primary and secondary transferssimultaneously and positively under the sole control of the accumulatordevices and without any 'addi-' tional presensing or final alignmentoperations.

It is still another object to provide in such machines: transfermechanism which effects all the primary .and secondary transferssimultaneously with each other, and proper final alignment of theaccumulator devices con currently with the simultaneous transferoperations. A further object is to provide in such machines transfermechanism which, in initiating primary transfers and in eifecting allprimary and secondary transfers simultaneously, is sufficiently positiveacting to be reliable in its operation.

A still further object is to provide in such machines transfer mechanismwhich effects all primary and secondary transfers simultaneously andaccurately, and yet is constructed simply and economically of componentswhich need not be engineered and manufactured to or maintained atextreme exact tolerances.

The invention involves providing in each denomina tional order of atransfer mechanism an accumulator device movable into a plurality ofitem storage positions, a transfer element movable therewith throughapredeter mined transfer distance and a transfer actuator. The transferelement of a first order in passing through such transfer distance isengageable with the transfer actuator of the next higher order. Underconditions where, during an item entering operation, the accumulatordevice moves through its transfer distance, its transfer element drivesthe actuator of the next higher order into what may be termed a transferaccept position, conditioning it for a primary transfer. Means areprovided for locking actuators thus moved into transfer accept positionto a transfer driving device which, when the accumulator devices are indriveable engagement with their respective 3 actuators, is effective todrive the actuators thus locked to a third position, effecting theprimary transfers. Under conditions where an accumulator device of anext higher order is itself, in turn, driven through its transferdistance by a primary transfer, its transfer element, in turn, engagesthe actuator of the next, next higher order, driving it towards transferaccept position to effect a secondary transfer simultaneously with theprimary transfers. Means individual to each actuator and operativelyresponsive to driven movement of its associated actuator towardstransfer accept position are also provided and are efiective forapplying to their respective actuators forces of sufiicient magnitudeand in a direction to move such actuators to transfer accept position tocomplete the secondary transfers and, simultaneously therewith, properalignment of the secondary transfer accumulators.

Features and advantages of the invention will be seen from the above,from the following descriptions of the preferred embodiments whenconsidered in conjunction with the drawings in which like numerals referto like parts in different figures, and from the appended claims.

In the drawings:

FIGURE 1 is a simplified diagrammatic cross-sectional view in sideelevation of a portion of a calculating machine embodying the inventionshowing one denominational order thereof with the parts in non-operatedcondition;

FIGURE 2 is an enlarged fragmentary end view of the transfer mechanismof FIGURE 1 looking from the right of FIGURE 1 showing various parts inoperated condition, and with the elements for the lowest to highestdenominational orders positioned consecutively from left to right;

FIGURE 3 is an enlarged fragmentary view of a portion of FIGURE 1showing the parts in condition for accumulating;

FIGURE 4 is a view similar to FIGURE 3 showing portions of the transfermechanism for two adjacent denominational orders with portions brokenaway and the transfer mechanism for one denominational order in transferaccept position; like parts of diiferent denominational orders beingdiflerentiated by the lower case suffix letters a and b appended totheir common numeral designations;

FIGURE 5 is a view similar to FIGURE 3 showing one denominational orderof the transfer mechanism with portions broken away, with transferactuator 41 in its fully operated position, and also fragmentaryillustrations of the actuator in its respective unoperated and transferaccept positions;

'FlGURE 6 is a view similar to FIGURE 3 of another embodiment of thesubject transfer mechanism, which embodiment is particularly suited forcalculating machines which add algebraically, showing in solid lineoutline the parts i in condition for accumulating, and in broken lineoutline a transfer actuator 41 in its transfer accept add position;

FIGURE 7 is a simplified schematic view of a portion of the mechanism ofFIGURE 6 showing a tarnsfer actuator 41 in its transfer accept subtractposition;

FIGURE 8 is a simplified schematic representation of a portion of thedrive mechanism for the add and subtract transfer bails 61a, 61s of themechanism of FIGURE 6, showing both bails in condition for accumulating;

FIGURE 9 is a view similar to FIGURE 3 of still another embodiment ofthe subject transfer mechanism showing in solid line outline the partsin condition for accumulating, and in broken line outline transferactuator 41 in both its transfer accept and fully operated positions;and k FIGURE 10 is a fragmentary rear end view of the transfer mechanismof FIGURE 9, looking from the right of FIGURE 9.

For the sake of simplicity and clarity, the invention is shown and willbe described as applied to calculating machines arranged foraccumulating items in decimal notation form, i.e. in powers of thenumeral 10, entered. by means of a 10 key keyboard and utilizing racksand pinion gears for listing the items and storing the accumulations; itbeing understood, nevertheless, that the invention is also applicable tomachines arranged for calculating items in denominational orders otherthan powers of 10, and utilizing other types of entering, listing andstoring mechanisms. Also for simplicity, zero, "0, will be termed adigit herein.

FiGURES 1 through 5 of the drawings illustrate a preferred embodimentparticularly suitable for calculating machines arranged for accumulatingitems unidirectionally only, such as, for example, machines which addbut do not subtract.

The adding machine illustrated is of the well known type consisting of apin box 11 (FIGURE 1), a set of horizontally arranged, longitudinallymovable racks 12 and coacting register pinion gears or accumulatorwheels 14; the mechanism for one denominational order only being shownin FlGURE 1.

The main drive shaft of the machine is designated 15. As is well knownin the art, this drive shaft makes one revolution at constant speed foreach machine cycle and, by known means, not here shown or described,imparts predetermined movements to various operating mechanism, such asuniversal bar 16 positioned in the forked end of actuating lever 17.Universal bar 16, during a first portion of the machine cycle, is causedto move to the right, travelling in longitudinally extending guide,slots 19 defined in the racks 12. Such movement releases the racks whichmay then also move linearly towards the right under the influence oftheir respective biasing springs 21. Racks 12 are guided in their linearmovements by means of rods 22, 23 fixedly positioned in guide slots 19,24, respectively.

As is usual in this type of machine, pin box 11 is mounted on a pincarriage (not shown) movable transversely of racks 12 step-by-step inresponse to each actuation of any of the input keys (not shown) of themachine. Pin box 11 is provided with a longitudinally extending row often pins 26 for each denominational order; the pins in each rowcorresponding to the digits 0 through 9 and being so designated. When afirst digit, for example 7, of an amount to be entered is set up in thekeyboard (not shown) the pin box is caused to move transversely one stepinto alignment with the rack 12 of the first denominational order, inthe present example, the rack for the units order. At the same time thepin 26, corresponding to digit 7 in the first pin row is moved downwardto act as a stop upon projection 23 of the rack 12 with which it is thenaligned. The pins 26 correspond ing to digit 9 are fixed in theirdownward positions and act as final limits to movement of the rackstoward the right. With the setting up on the keyboard of each subsequentdigit of the amount to be entered; a corresponding digit pin 26 isdepressed in a successive pin row in accordance with such amount; pinbox 11 continuing its step-by-step transverse movement at each input,thereby placing, as the last digit is entered, each depressed pin intoproper alignment with the rack 12 associated with its denominationalorder in accordance with the most significant number of the amount to beentered. A suppressor member 3! movable with pin box 11 projects in thedirection of pin box movement, and, in a well known manner, coacts withprojection 28 of the racks 12 associated with denominational ordersgreater than the most significant number of the amount to be entered,preventing the release of such racks.

When universal bar 16, in moving to the right, releases racks 12, theymove under the influence of their respective biasing springs 21 to theright. The movement of the racks for which an input has not been set upis arrested, as has been explained previously, by rack suppressor 3dengaging their respective projections 23. Each of the racks into which adigit is to be entered continues moving or escapes to the right untilarrested by the pin 26 set into the path of its projection 28.

Thus, it may be seen that the arrested position of each rack 12 whichescapes is determined by the relative position of its arresting pin 26with respect to the other pins in the same pin row, and indicates thedigit corresponding to such arresting pin. The amount to be stored andaccumulated by the machine has now been, What may be termed, enteredinto the racks.

The mechanism for storing and accumulating the entered amount comprisesfor each denominational order a pinion gear 14, having as manyperipheral teeth 33 as there are possible inputs into its order. For thepresent example of accumulations in decimal notational form, each piniongear 14 is provided with ten teeth 33 spaced 36 apart and correspondingto the digits 0 through 9. Pinion gears 14 are rotatably mounted onshaft 35, and are normally held out of engagement with coasting teeth 37formed on their respective associated racks 12. Each pinion gear 14 isprovided with an axially projecting side or transfer tooth 39 (FIGURES land 2), for purposes to be explained hereafter.

A set of transfer actuators 41, one for each denominational order, arepivotally mounted on a fixed shaft 43. However, the actuator 41 for thelowest order is prevented from pivoting by rod 42 (FIGURE 2) rigidlysecuring such actuator to a fixed side wall 44 of the machine. Eachtransfer actuator 41 consists of a segmental gear portion 45, havingthree teeth 47 spaced 36 apart and facing the pinion gear 14 associatedwith its denominational order (with whose peripheral teeth 33 they arealigned for meshing cooperation) and a transfer pawl portion 49 offsetfrom the segmental gear portion 45 and extending towards the piniongears 14 for cooperating with the transfer tooth 39 of the pinion gear14 of the next lower order. An additional transfer actuator 41 without asegmental gear portion 45 is also provided, and is positioned on theright end of fixed shaft 43 (FIGURE 2) so that its transfer pawl portion49 may cooperate with the side tooth 39 of the pinion gear 14 of thehighest order, for purposes to be explained hereinafter. Spacers 38 and41) (FIGURE 2) rotatably mounted on shafts 35 and 43, respectively,maintain pinion gears 14 and transfer actuators 41 in proper alignmentwith each other.

A set of toggle springs 51, one for each transfer actuator 41, areprovided. Each toggle spring 51 has two attaching ends, one of which isattached to a fixed shaft 53, common to all the springs, and the otherof which is attached to projecting arm 55 of its associated transferactuator 41. Under conditions where the transfer actuators 41 are intheir respective non-operated or rest positions I (FIGURE 1), they areindividually urged by their respective toggle springs 51 against a stop57 in the form of a fixed rod common to all the transfer actuators.

Mechanism for driving the transfer actuators, in a manner to bedescribed hereinafter, is provided and includes a transfer bail 61 ofU-shaped configuration (FIG- URE 2) rotatably mounted at its bent overend portions 59, 60 on fixed shaft 43. Transfer ball 61 is actuatedwithin a limited arcuate path in a predetermined manner during themachine cycle by means of a cam follower arm as, cooperating with a cam67 mounted on an auxiliary drive shaft 69 driven from main drive shaft15. Bail 61 is pivotally connected at its bent over end portion 60 toone end of cam follower arm 63 by means of a short shaft 64 (FIGURE 2),the other end 65 (FIGURES l, 2) of which cam follower arm is pivotallysecured to stationary side wall 44 of the transfer mechanism. A camfollower 72 is rotatably mounted on cam follower arm 63 and is biased byspring '74 (FIGURE 1) into rolling engagement with the cam surface ofcam 67 for actuation of the cam follower arm and, in turn, bail 61.

An axially extending transfer bar 78 is carried by bail 61. Formed ineach bent over end portion 59, 60 of bail 61 is a radially extendingguide slot 76 (FIGURE 1) into which transfer bar 78 is disposed forlimited radial movement. Transfer bar 78 also extends through arcuatecam slots 81 formed in the oppositely disposed stationary side walls 44,83 (FIGURE 2) of the machine. Bail 61, in its movements, carriestransfer bar 78 along arcuate cam slots 81 which act to limit arcuatemovement of the bail. A radially disposed coil spring 86 (FIGURE 5),under tension, biases transfer bar 78 inward toward shaft 43 of thetransfer actuators 41, causing the transfer bar, as it travels in camslots 81, to ride along the inward edge cammin-g surfaces 90 of such camslots thereby moving radially within radial guide slots 76 as ittravels.

It may be noted that each transfer actuator 41 has formed on its sideedge surface adjacent transfer bar 73 a camming projection 93 and atransfer bar receiving cut-out portion 95 (FIGURE 3); they beingprovided for cooperation with the transfer bar, in a manner and forpurposes to be explained hereinafter. In addition, the midsection ofarcuate cam slot 81 is slightly enlarged to allow limited radialmovement of transfer bar 78 within such slot section, for purposes alsoto be explained hereinafter. As will be apparent from the drawings,transfer bar 78 may be carried clockwise by bail 61 from its restposition, designated I (FIGURE 1) along arcuate cam slot 81 to amidposition II (FIGURE 3) and then to a third position III (FIGURES). Bail61, during its return stroke, carries transfer bar 78 counterclockwiseback to its rest positionI.

During the escape of racks 12 to the right, previously described, andwhich occurs during the amount entering portion of the machine cycle,pinion gears 14 are held in engagement with their'corresponding transferactuators 41 (FIGURE 1) and out of engagement with racks 12. Next in thecycle, bail 61 is driven to position II (FIGURE 3), carrying transferbar 78 along with it into the slightly enlarged midsection ofarcuate'cam slot 81. Pinion gears 14 are then moved out of engagementwith their respective transfer actuators 41 and into engagement withtheir corresponding racks 12 (FIGURE 3) 'in preparation for transferringthe amount (presently entered into the racks) into pinion gears 14 forstorage. The mecha nism for moving pinion gears 14 between theirrespective transfer actuator engaging positions and rack engagingpositions is well known in the art, and, therefore has not been shownand will not be described herein.

It may be noted that racks 12, pinion gears 14.and transfer actuators 41are positioned with respect to each other such that pinion gears 14engage rack teeth37 of their respective corresponding racks before theybecome entirely disengaged from the segmental gear portions 45 of theirrespective associated transfer actuators 41. Such relative positioningobviates unintended slip rotation of pinion gears 14, while they arebeing disengaged from transfer actuators 41 and engaged with racks 12,or vice versa, which slip rotation may result in the incorrect storageof accumulations.

The racks 12, which have escaped to the right to predeterminedrespective positions corresponding to the amount entered therein, arenext driven by universal bar 16 leftward back to their respectivenormally non-operated positions. These racks, in moving leftward, rotatetheir corresponding pinion gears 14 with which they are presentlymeshed, counter-clockwise predetermined amounts in accordance with theirown respective linear movements. Such translation of the linear rackmovement to rotational gear movement transfers the amount previouslyentered into the racks into their corresponding pinion gears forstorage.

It may be noted that the transfer pawl portion 49 of each transferactuator 41 is positioned with respect to the side tooth 39 carried bythe pinion gear 14 of the next lower order so as to be engaged therebywhenever such pinion gear has accumulated to the digit 9 in itsdenominational order.

Next assume that a pinion gear 14 of a certain denomination is rotatedcounter-clockwise by its corresponding rack 12 one unit past its storagecapacity, in the present example 9, necessitating that its accumulatedtotal be transferred, as a unit, to the pinion gear of the next higherorder. In such a case, as such certain pinion gear 14 is thus rotatedthrough what may be termed its transfer position or arc its side tooth39, presently in engagement with the transfer pawl portion 4% of thetransfer actuator 41 of the next higher order, drives such transferactuator clockwise one step to position If (FIGURE 4), which positionmay be termed the transfer accept position, in preparation for effectinga primary transfer to the pinion gear 14 of the next higher order.

As transfer actuator 41 is thus rotated from its rest position I (FIGURE3) to position II, its toggle spring 51 (FIGURE one end of which isattached to the actuator, is moved off center sufiiciently so as toapply its biasing force to actuator il in a direction to aid theclockwise movement of the actuator. In addition, as transfer actuator 41rotates clockwise toward position II, its camming edge surface 93engages transfer bar 73, pushing it outward, against the force ofbiasing coil spring 856 out of engagement with the inner cam surface 90of arcuate cam slot 81, thereby causing bar 78 to ride along cammingedge surface 93. Upon movement of actuator 41 to position II, coilspring 86 urges transfer bar 78 into cut-out portion 95- of theactuator, thereby effectively locking the transfer actuator to thetransfer bar in the transfer accept position. it may thus be seen thatany transfer actuator 41 which is rotated to transfer accept position IIin preparation for effecting a primary transfer becomes, in suchposition, locked to transfer bar '78.

Pinion gears 14 (FIGURE 5) are next moved out of engagement with theirrespective racks 12 and back into engagement with the segmental gearportions 45 of their corresponding transfer actuators 41. Transfer bail61 is then driven clockwise by its operating mechanism from position IIto position III, driving the prepared transfer actuators 4]. (locked totransfer bar 78 in position II) clockwise from transfer accept positionII to position III, thereby rotating the pinion gears M, presentlymeshed with such prepared actuators, counter-clockwise one step toeffect the primary transfers.

Next assume that a transfer actuator 41, in rotating from position II toIII to effect a primary transfer t the pinion gear 14 of a next higherorder, drives such higher order pinion gear, in turn, through itstransfer position. This necessitates a secondary transfer of theaccumulation of such higher order pinion gear to the pinion gear 14 ofthe next, next higher order. In such a case, as the pinion gear 14 ofsuch next higher order is rotated counter-clockwise through its transferposition, its side tooth 39, presently in engagement with the transferpawl portion of the transfer actuator 41 of the next, next higher order,drives such actuator clockwise one step from its rest position I toposition II. Actuator 41 of such next, next higher order in rotatingclockwise one step, in turn, drives its corresponding intermeshed piniongear 14, one step counter-clockwise, thereby effecting a secondarytransfer thereto simultaneously with the aforementioned primarytransfer. As was previously described, transfer actuator 41 in rotatingfrom position I to II moves its toggle spring 51 off center sufiicientlyto cause such spring to exert in a snap action manner its biasing forcein a direction to aid the secondary transfor for purposes to beexplained hereinafter.

Next assume that the pinion gear 14 of such next, next higher order isalso thus rotated through its transfer position, causing its side tooth39, in turn, to drive the transfer actuator 41 of the next successivehigher order to position II, thereby effecting another secondarytransfer simultaneously. It may therefore be seen that, under certainconditions, a series of secondary transfers may occur simultaneously.For example, in the case of the digit 1 being added to the numeral99999, it is seen that a primary transfer occurs from the first to thesecond orders, and concurrently therewith secondary transfers occur tothe third, fourth and fifth orders. Since it is seen that all thetransfers are effected by hail of being driven from position II toposition III, it is apparent that they are all (both primary andsecondary and in all orders) effected simultaneously with each other.

It may be noted that the pinion gears 14 instrumental in the aboveexample to effect a series of concurrent secondary transfers may, due tooperating tolerances necessarily provided between transfer actuators 4iand pinion gears 14, be moved less than one full step during thetransfer operation, and, therefore, not be properly aligned at thecompletion of the transfers. In order to remove such a possibility,toggle springs 51 individual to the transfer actuators 41, areeffective, during movement of the transfer actuators from position I toII, to exert individually on their respective transfer actuators snapaction forces sufficient in magnitude and in a direction to drive suchactuators to position II. The application of these individual snapaction spring forces to actuators 41 causes rotation of the pinion gears14 with which the actuators are then meshed a full step into properalignment. In efiect, such individual toggle springs 51 act as a snapaction" despiraling device in cases of successive secondary transfers toobtain, simultaneously with the transfer operations, accurate finalalignment of pinion gears 14- and, consequently, correct storage of theamount entered. The springs 51 are especially useful whenever a seriesof concurrent secondary transfers occurs.

In order to return the transfer mechanism to its normally unoperatcdcondition in preparation for the next operation without affecting thepresent data storage positions of pinion gears 14, the pinion gears areagain moved out of engagement with their corresponding tran feractuators 41 and back into engagement with racks 12. Bail 61 is thendriven through a counter-clockwise return stroke from position III toposition, I, driving any previously actuated transfer actuators 41 backto their rest positions against stop 57. As transfer actuators 41 arethus returned to rest position, transfer bar 78, carried by bail 61,rides along the inner camming edge surface 9% of cam slot 81, moving asit travels past the midsection of slot 81, out of locking engagementwith transfer actuators 4i. Pinion gears 14 are then returned intoengagement with their corresponding transfer actuators .41 inpreparation for the next operation of the machine.

During total taking, the respective pawl portions 49 of transferactuators 41 in cooperation with their corresponding side teeth 39 ofthe pinion gears 14 act as Zero stops for the pinion gears, as is wellknown in the art; the transfer pawl 49 (FIGURE 2) for the highestdenominational order (which pawl, as was previously stated, is not partof a transfer actuator) acting as a zero stop for the pinion gear 14 ofsuch highest order.

In order to illustrate the operation of the present transfer mechanismassume that the amount of 61,579 has been entered into racks 12, in amanner similar to that previously described, and is to be added to theamount 563,439 already accumulated in pinion gears 14. Under suchconditions, pinion gear 14 for the first order has already accumulatedits storage capacity, i.e. to 9 and its side tooth 39 is presently inengagement with the transfer pawl portion as of the transfer actuator 41for the second denominational order. Next assume that the amount 61,579is transferred from racks 12 to pinion gears 14 for storage by drivenreturn movement of the previously escaped racks to the left, as waspreviously described. Such rack movement drives the pinion gears 14 forthe first, second and fifth orders counterclockwise beyond theirrespective 9 positions, causing their respective side teeth 39 to engagethe drive the transfer pawl portions 49 of their respective next higherorder transfer actuators 41 clockwise from rest position I to transferaccept position II in preparation for effecting primary transfers to thesecond, third and sixth order pinion gears 14. Thus, after the amounthas been entered into the pinion gears 14 for storage but before thetens transfers have occurred, the transfer actuators 41 associated withthe second, third and sixth denominational orders are in transfer acceptposition If and locked to transfer bar 78.

Next, pinion gears 14 are moved into meshing engagement with thesegmental gear portions 45 of their corresponding transfer actuators 41,and transfer bail 61 is driven clockwise from position If to III,driving (by means of transfer bar 78) the prepared transfer actuators 41to position III, thereby effecting primary transfers to the second,third and sixth orders by driving the pinion gears 14, corresponding tosuch prepared transfer actuators, counter-clockwise one step. Moreover,since the pinion gear 14 for the third order, in receiving the unit ofprimary transfer from the second order, in turn, moves from its 9 topositions, its side tooth 39 engages the transfer pawl portion 4) of thetransfer actuator 41 associated with the fourth order, driving itclockwise to position II. Rotation of the transfer actuator 41 for thefourth order to position II drives its intermeshed corresponding piniongear 14 one step counterclockwise, efiecting a secondary transfer to thefourth order pinion gear. In addition, as the transfer actuator 41 ofthe fourth order moves from position I to 11, its toggle spring 51 ismoved off center sufiiciently to exert a snap action spring force in adirection to aid clockwise movement of such transfer actuator toposition II and of sufficient magnitude to effect proper alignment ofpinion gear 14 for the fourth order, thereby correctly storing theaccumulated total amount 625,018 in the pinion gears.

In FIGURES 6 through 8 is illustrated a slightly modified embodiment ofthe add only transfer mechanism of FIGURES 1 through 5, which modifiedembodiment is particularly suitable for calculating machines arrangedfor accumulating items algebraically, i.e., machines which not only addbut also subtract. The algebraic embodiment of FIGURES 6 through 8 issimilar in construction and operation to that of the add onlyembodiment, previously described. For the sake of brevity and clarity,similar elements of both embodiments bear the same numeral designations;the sufiix letters a and s being added to the numeral designations inFIGURES 6 through 8 of elements which are utilized for adding andsubtracting, respectively, to differentiate therebetween. For example,the rack in FIGURE 6 is designated 12, as it is in FIGURES 1 through 5,and, in FIGURE 6, 61a designates an add transfer bail while 61sdesignates a second bail, termed a subtract transfer bail; both bailsbeing similar in construction and operation to transfer bail 61 of theadd only embodiment of FIGURES 1 through 5.

Transfer bail 61a for adding and transfer bail 61s for subtracting arearranged to be simultaneously driven during predetermined portions ofthe machine cycle from their respective rest positions I, to transferaccept positions II and then to transfer complete positions III. Themechanism for driving transfer bails 61a, 61s simultaneously isrepresented schematically in FIGURE 8 wherein 63 designates a camfollower arm cooperating with a cam 67 mounted on auxiliary drive shaft69 which, in turn, is driven from main drive shaft (not shown). Camfollower arm 63 is mounted on the calculating machine frame (not shown)to pivot at 101, and has formed on one of its ends a segmental gearportion 193 which is intermeshed with a segmental gear portion 195formed on an auxiliary cam follower arm 1G7. Arm 107 is also mounted onthe machine frame to pivot at 169. Add bail 61a has a driven portion 62aconnected to the driving end of cam follower arm 63 by means of a shortstub shaft 111a positioned in an elongated slot 113a defined in the camfollower arm. Subtract bail 61s has a driven end 62s similarly attachedto auxiliary cam follower arm 107 by means of short stub shaft 111spositioned in elongated slot 113s formed in the driving end of auxiliarycam follower arm 167.

Clockwise rotation of cam follower arm 63 by cam 67 causes simultaneouscounter-clockwise rotation of auxiliary cam follower arm 107 with whichit is intermeshed. Such follower arm movement drives transfer bails 61a,61s simultaneously, during predetermined portions of the machine cycle,from their respective rest positions designated I to positions II and,finally, to positions III. Counter-clockwise movement of cam followerarm 63, during the machine cycle, and corresponding clockwise movementof auxiliary cam follower arm 167 returns bails 61a, 61s to theirrespective rest positions I in preparation for subsequent reoperation.

A dog eared member 115 is provided for each transfer actuator 41; thedog eared members 115 being rigidly attached to a common manuallyrotatable shaft 117 supported on the calculating machine frame (notshown). Shaft 117 may be manually rotated into either of two positions,depending upon whether an add or subtract operation is desired. Withmembers 115 in what may be termed their respective add positions, asshown in FIG- URE 6, the members 115 limit counter-clockwise movement oftheir respective associated transfer actuators 41 by means of a lateralstop projection 57a formed on the right ear of each member. When the dogeared members 115 are rotated clockwise into subtract position (FIGURE7), a similar stop projection 57s formed on the left ear of each memberlimits clockwise movement of their associated transfer actuators 41.

Toggle springs 51, one for each transfer actuator 41, are pivotablyattached at one end to a common spring shaft 53 which is, in turn,rigidly attached to the respective mid portions of dog eared members 115for movement therewith. With dog eared members 115 in position foradding (FIGURE 6), toggle springs 51 urge their respective transferactuators 41 against their corresponding stops 57a, while with dog earedmembers 115 in position for subtracting (FIGURE 7) springs 51 urge theirrespective transfer actuators 41 against their c0rresponding stops 57s.

As may be seen from FIGURE 6 (wherein the parts are shown in conditionfor accumulating, additively), the racks 12, pinion gears 14 andtransfer actuators 41 for each denominational order may each be drivenin either of two opposite directions, depending upon whether an amountis to be accumulated additively or subtractively; the proper directionsbeing indicated by appropriately designated directional arrows. Upon arack 12 being driven to the left (in any well known manner) apredetermined linear distance in accordance with the amount to beaccumulated additively in its order, its corresponding pinion gear 14 isrotated counter-clockwise a corresponding distance, thereby entering theamount additively into the pinion gear for storage. Each pinion gear 14is provided with a side tooth 39 in position for engaging and drivingtransfer pawl portion 49 of the transfer actuator for the next higherorder as the pinion gear passes through its transfer position eitheradditively or subtractively; each portion 49 being dimensioned in Widthas to be engaged by its associated side tooth 39 as such side tootharrives at transfer position either additively or subtractively. R0-tation of pinion gear 14 counterclockwise through its transfer positioncauses the right or add side edge of its side tooth 39 to engage theleft side edge of transfer awl portion 49 of the transfer actuator 41 ofthe next high order, driving such transfer actuator clockwise from itsrest position I to its transfer accept position II in preparation foreffecting a primary transfer to the pinion gear of such next higherorder. Each actuator 41 has formed on its lower left side edge surface acamming projection 93a and a transfer bar receiving cut-out portion 95afor cooperation with add transfer bar 1 8a to lock transfer actuator 41to the transfer bar when the actuator is rotated clockwise to transferaccept position If for additive accumulations, in a manner similar tothat previously described for the add only machine.

Racks 12 may similarly be driven to the right predetermined lineardistances in accordance with the amount to be accumulated subtractivelyin their respective orders. Such driven movement of racks 12 to theright drives their associated pinion gears 14 clockwise correspondingrespective distances, thereby accumulating the amount therein forstorage. Under conditions where such a pinion gear 14 passes through itstransfer position subtractively, the left or subtract side edge of itsside tooth 39 engages the right side edge of transfer pawl portion 49 ofthe transfer actuator 41 for the next higher order, driving such nexthigher transfer actuator counterclockwise from its rest position I totransfer accept position II (FIGURE 7) where it becomes locked tosubtract transfer bar 78s, in a manner similar to that previouslydescribed for additive accumulations, in preparation for effecting aprimary transfer subtractively to the pinion gear 14 of such next higherorder.

In operation, assume that it is desired to accumulate a certain amountadditively. Dog ear-ed member 115 is manually moved to its acid position(FIGURE 6) and pinion gears 14 are disengaged from racks l2 and movedinto engagement with their respective segmental gear portions 45 oftheir corresponding transfer actuators 41. Next in the machine cycle,the add and subtract bails 61a, 61s, respectively, with their respectivecorresponding transfer bars 78a, 78s are driven simultaneously fromtheir rest positions I to their respective positions II, and certainracks 12 allowed to escape to the right predetermined respectivedistances in accordance with the amount to be entered therein.

Next, the pinion gears 14 are moved out of engagement with theirassociated transfer actuators 41 and into engagement with theircorresponding racks 12. The escaped racks 12. are next driven to theleft to their original respective unoperated positions, rotating theirrespective intermeshed pinion gears 14 additively (counter-clockwise)corresponding distances, thereby placing the amount to be accumulatedadditively into the pinion gears 14 for storage.

In order to demonstrate the operation of the transfer mechanism foradditive accumulations, next assume that, as a pinion gear 14 is rotatedadditively (counter-clockwise by movement of its associated rack I2 tothe left), it passes through its transfer position. Under suchconditoins, as it passes additively through its transfer position,

the add side edge of its side tooth 39 engages and drives the trans'erpawl 49 of the transfer actuator 41 of the next higher order oneposition clockwise, rotating such next higher order transfer actuator 41from its rest position I to transfer accept position II, where itbecomes locked to add transfer bar 78a in preparation for effecting aprimary transfer additively; toggle spring 51 aiding such movement ofthe transfer actuator.

Next in the machine cycle, pinion gears 14 are moved out of engagementwith racks 12 and into engagement with their corresponding transferactuators 41. Transfer bails 61a, 61s are then simultaneously moved fromtheir respective positions II to III; add transfer bar 78a (carried bybail 61a), driving the next higher order transfer actuator 41 (which islocked to it) from position II to III to effect additively a primarytransfer to the next higher order, as has been previously described(such movement of transfer actuator 41 from position II to III, causingit to drive its corresponding pinion gear 14, with which it is presentlyintermeshed, one position counteri2 clockwise to transfer theaccumulation, as a unit, additively to the next higher order piniongear). It may be noted that, during such transfer operation, themovements of subtract bail 61s and its associated transfer bar 78s arewithout effect.

As was previously described for the add only machine, should the piniongear i i of such next higher order, in turn, be rotated by the primarytransfer counterclockwise past its transfer position, the add side edgeof its side tooth 39, in turn, engages the transfer pawl portion 49 ofthe transfer actuator 41 for the next, next higher order, driving suchnext, next higher actuator 41 from its rest position I to position II.Such movement of the next, next actuator 4-1, in turn, drives itscorresponding pinion gear I4 (with which it is presently intermeshed)one position counter-clockwise, effecting an additive secondary transferto the pinion gear 14 of such next, next high order simultaneously withthe primary transfer.

As has been previously described, upon movement of of such next, nexttransfer actuator 41 from its position I to II to effect a secondarytransfer, its associated toggle spring 51 is moved off centersufficiently to exert a snap action spring force on such transferactuator in a direction and of sufficient magnitude to propel itscorresponding pinion gear 14 into proper final alignment simultaneouslywith the effecting of the primary and secondary transfers.

During subtractive accumulations, subtractive primary and secondarytransfers are effected in a similar manner. To effect subtractiveaccumulations and transfers, dog eared member is manually rotatedclockwise to its subtract position (FIGURE 7), moving toggle springs 51into a position where they bias their associated transfer actuators 41against their corresponding stops 57s. Certain of the racks 12 aredriven to the right predetermined respective linear distances,corresponding to the amount to be accumulated su'otractively, drivingtheir corresponding pinion gears 14 clockwise corresponding distances,thereby accumulating the amount subtractively therein for storage.

Next assume that a pinion gear 14 is rotated subtractively (clockwise)through its transfer position. Under such circumstances, the subtractside edge of its side tooth 39 engages the right side of the transferpawl portion 49 of the transfer actuator ill of the next higher order,driving it counter-clockwise from its rest position I to transfer acceptposition II (FIGURE 7), where it becomes latched to subtract transferbar 7hr in preparation for effecting a primary transfer. It may be seenthat upon pinion gears 14 being moved out of engagement with theircorresponding racks I2 and into engagement with their correspondingtransfer actuators 41, and upon simultaneous driven movement of thetransfer bails 61a, his and their associated transfer bars 78a, '78sfrom position II to HI, all transfer actuators 41 which are presentlylocked to subtract transfer bar 78s are moved to position III,reflecting the necessary primary and secondary transfers, in a mannersimilar to that previously described for additive accumulations; togglesprings 51, during secondary transfers, now acting to urge transferactuators ll involved in secondary transfers counterclockwise fromposition I to position II, exerting a snap action, spring force ofsuflicient magnitude to properly finally align pinion gears 14simultaneously with the effecting of the primary and secondarytransfers.

If it is desired, stop projections 57a, 57s of dog eared member 115 maybe omitted, and, during additive accumulations and transfers, subtractbail 61s and its transfer bar '78s disengaged from the bail drivingmechanism and held immobile in their rest positions I to act as a stop,limiting counter-clockwise movement of transfer actuators 41; and viceversa, during subtractive accumulations and transfers.

FIGURES 9 and 10 show the subject transfer mechanism slightly modifiedfor use in calculating machines equipped with accumulators of the wellknown two pinion gear type for algebraic addition. Accumulator 172 is analgebraic type, comprising a pair of constantly intermeshed accumulatingpinion gears 14, 15 for each denominational order. The pinion gears arerotatably mounted on fixed pinion shafts 35 on a carriage 1'75. Carriage175 may be rotated through 180 to pre;ent either of pinion gears 14, 15to their corresponding racks (not shown) for receiving from the racksthe amount to be stored and accumulated. Normally, accumulator 172 isheld out of engagement with the racks while the amount to be accumulatedand stored by the pinion gears is entered into the racks during e:capemovement of the racks, in a manner similar to that previously describedfor the add only machine; it being understood however, that for thesubject embodiment escape movement of the racks is to the left.Accumulator 172 is then moved into engagement with the racks, and theracks driven to the right to transfer the amount from the racks to theircorresponding pinion gears 14, 15 for storage.

With pinion gears 14, 15 in rack engaging position, as shown in FIGURE9, the amount to be accumulated is added into the pinion gears by theracks driving the top pinion gears 14 clockwise. Upon reversal ofcarriage 175 through 180", the bottom pinion gears 15 are placed intoengagement with the racks and are rotated clockwise thereby to subtractthe amount, thus transferred, from the amount previously stored andaccumulated in pinion gears 14, 15; the direction of rotation of therespective pinion gears 14, 15 for adding and subtracting beingindicated by appropriately dsignated directional arrows. The mechanismfor rotating carriage 175 through 180 to present either the add orsubtract pinion gears 14, 15, respectively, to the racks, and themechanism for shifting accumulator 172 into and out of rack engagingposition are both well knownin the art and therefore will not bedescribed herein.

Each pinion gear 14, 15 is provided with a side tooth 39. A set ofarcuate shaped transfer index levers 177, one for each pair of piniongears 14, 15 are pivotally mounted intermediate their respective ends ona common fixed shaft 179. The upper arm of each index lever 177 hasformed at its end a pawl portion 181 for engaging the side tooth 39 ofits corresponding pinion gear (14, 15, as the case may be) when suchpinion gear is in rack engaging position. The other arm of each indexlever 177 has also formed at its end a pawl portion 183, and is slightlybent in a lateral direction to position pawl portion 183 into engagementwith a gear tooth 4'7 of the segmental gear portion 45 of a transferactuator 41 provided for the next higher order. A set of leaf springs185 is provided, one for each index lever 177 and fixedly mounted inposition to bias its corresponding lever counter-clockwise into sidetooth engaging position (shown in FIGURE 9 in solid outline). Transferactuators 41 are rotatably mounted on a common fixed shaft 43. Spacers190 (FIGURE 10) are provided on actuator shaft 43, pinion shafts 35 andlever shaft 1'79 to properly align the pinion gears 14, 15, levers 177and actuators 41 with each other.

The segmental gear portion 45 of each transfer actuator 41 is providedwith a side tooth 193, projecting laterally in a direction forengagement with side tooth 39 of the pinion gear (14, 15, as the casemay be) provided for v the next lower order, under conditions whereaccumulator 172 is moved downward into engagement with segmental gearportions 45 of transfer actuators 41.

It may be seen that the remainder of the transfer mechanism of FIGURES9, 10 is similar in structure and operation to that provided for thepreviously described add only embodiment shown in FIGURES 1-5, i.e.,bail 61 may be driven from position I to 11, carrying transfer bar 78with it along arcuate guide slots 81. Transfer bar 78 when in positionII is efiective by means of its biasing spring 86 and the radial guideslot 76, re cessed portion 95 and camming surface 93 formed in eachtransfer actuator 41 to lock the transfer actuators 41 which are rotatedinto transfer accept position, as will be described hereinafter, to bail61. Bail 61 may then be driven from position 11 to III to effect theprimary and secondary transfers simultaneously, as will be describedhereinafter. Toggle springs 51, one for each transfer actuator 41 areeffected; as was previously described, in response to clockwise movementof their associated trans fer actuators 41 from position I to II toexert individual snap action spring forces on their respective transferactuators 41 to aid their movement to position II.

Assume that an amount is to be transferred additively from the racks(into which it has been previously entered) into accumulator 172 forstorage. Under such conditions, accumulator 172 is in its add position(i.e. with pinion gears 14 in their upper positions) and is moved intoengagement with the racks (not shown) while bail 61 is driven clockwiseto position 11, carrying transfer bar 78 with it. Next, the racks aredriven to the right back to their normally non-operated positions,rotating their corresponding top pinion gears 14 clockwise in accordancewith the amount previously entered to transfer such amount to piniongears 14, in turn, driving their respective inter-meshed bottom piniongears 15 counter-clockwise like amounts.

Next assume that one of the top pinion gears 14 is rotated by itscorresponding rack through its transfer position or are. As such piniongear 14 moves through its transfer are of 36, its side tooth 39constantly engages top pawl portion 181 of its associated index lever177 causing such lever to pivot clockwise (as shown in FIG- URE 9 inbroken line outline) about its pivot point against the biasing force ofleaf spring 185-. This pivotal movement of index lever 177 positivelydrives, by means of lower pawl portion 183 of the lever, the transferactuator 41 for the next higher order clockwise one step into transferaccept position 11, in preparation for a primary transfer. As suchtransfer actuator arrives at position II, it becomes locked to transferbar 7 8, as was previously described. In addition, movement of suchactuator 41 from position I to position If at the same time causes itstoggle spring 51 to be moved off center sufiiciently to exert its springforce in a snap action fashion in a direction to aid clockwise rotationof the transfer actuator.

Next, accumulator 172 is moved into engagement with transfer actuators41; its bottom pinion gears 15 meshing with the segmental gear portions45 of their respective corresponding actuators 41. Bail 61 is thendriven clockwise from position If to ill to effect the primary transfersby rotating the aforementioned next higher order transfer actuator 41(presently locked to transfer bar 78) to position HI. Such transferactuator in rotating clockwise from position II to H1 drives the bottompinion gear 15 with which it is presently engaged counter-clockwise onestep to transfer one unit additively thereto, thereby effecting aprimary transfer to the aforementioned next higher order pinion gears.

Next assume that the bottom pinion gear 15 of such next higher order is,in turn, moved through its transfer are by the primary transfer. In sucha case, its side tooth 39 engages the side tooth 193 of the transferactuator 41 for the next, next higher order, driving it clockwise onestep from position I to II. Such transfer actuator 41, in turn, rotatesthe pinion gear 15 of such next, next higher order, with which piniongear it is presently intermeshed, one step, counter-clockwise effectinga secondary transfer to the next, next higher order pinion gears 14, 15simultaneously with the previously described primary transfer to thenext higher order pinion gears 14, 15. At the same time, toggle spring51 of such next, next higher order transfer actuator 41, as has beenpreviously described, is moved sufficiently ofi center by rotation ofits transfer actuator 41 clockwise frorn'position I to H 15 to apply asnap action spring force to such transfer actuator in a clockwisedirection. Toggle springs 51 are selected so as to exert snap actionforces of sufficient magnitude to drive the pinion gears l4, 15, withwhich their respective transfer actuators 41 are intermeshed, into finalproper alignment for correct storage of the amount accumulated therebyTo prepare the calculating machine for its next operation, accumulator172 is again disengaged from transfer actuators d1, and hail 61 isdriven counter-clockwise through its return stroke back to rest position1, thereby also returning the previously actuated transfer actuators 41to rest position I.

It may be seen from FIGURES 9 and 10 of the drawingsthat, upon rotationof accumulator carriage 172 through 180 to present pinion gears to theracks and upon operation of the subject transfer mechanism in a mannersimilar to that previously described for adding an amount entered to theamount previously stored and accumulated by pinion gears 14, i5, anamount entered into the racks will be subtractively transferred from theracks to pinion gears 14, 15 and any required primary and secondarytransfers effected simultaneously with each other and with finalproperalignment of the pinion gears.

As many changes could be made in the above construction and manyapparently widely different embodiments ofthis invention could be madewithout departing from the scope thereof, it is intended that all mattercontained in the above description or shown on the accompanying drawingsshall be interpreted as illustrative and not in a limiting sense.

What'is claimed is:

I. In a simultaneously operable transfer mechanism for calculatingmachine registers having in each denomirrational order a register wheeland a transfer element rotatable therewith through a transfer position;a transfer actuator arranged for driving engagement with-the wheel "ofthe next higher order and having an integral portion extending intoposition for rotation of said actuator by said transfer element in adirection opposite to the direction of rotation of said register wheelunder conditions where said transfer element is rotated through saidtransfer position, said transfer element rotating said actuator in saidopposite direction from a normal position to a second position; saidactuator being furthermore movable in said opposite direction from saidsecond position to third position; a driving bar common to saidactuators and operable, during driving engagement of said actuators withtheir respective higher order wheels, for rotating the actuatorspositioned in said second position to said third position effectingprimary and secondary transfers simultaneously; and a plurality of geardespiraling means individual to said actuators and responsive tomovement of their respective actuators from said normal position to saidsecond position, each of said despiraling means effecting properalignment of the register wheel with which its associated actuator isengaged during a secondary transfer operation.

2 A- transfer mechanism as set forth in claim 1 wherein latching meansare provided for establishing individual latching connections betweensaid actuators and said driving bar, said latching means beingoperatively responsive to rotative movement of their associatedactuators from said normal to said second positions under conditionswhere said actuators are out of driving engagement with their respectivehigher order wheels.

3. A transfer mechanism as set forth in claim" 1 wherein said pluralityof gear despiraling means individual to said actuators each includes atoggle spring operably connected to its associated actuator andmaintained in compression, said toggle spring being effective, uponmovement of its associated actuator from said normal position towardssaid second position, to apply a snap action spring force to saidassociated actuator aiding such movement.

4, In a simultaneously operable transfer mechanism for calculatingmachine registers having in each denomirrational order a register wheeland a transfer element rotatable therewith through a transfer position;a transfer actuator arranged for driving engagement with the wheel ofthe next higher order and having an integral portion extending intoposition for rotation by said transfer element in a direction oppositeto the direction of rotation of said register Wheel; said transferactuator, under conditions where said transfer element rotates throughsaid transfer position and said actuator is disengaged from itsassociated wheel, being rotated in said opposite direction from a normalposition to a set position for conditioning a primary transferoperation; said actuator being furthermore movable from said setposition to third position in said opposite direction; said actuatorwhen in normal position and during engagement with said higher orderwheel and, under conditions where said element of the next lowerregisterwheel is rotated through said transfer position, being moved by saidnext lower element into said set position simultaneously with saidrotation to effect a. secondary transfer operation; a driving bar commonto said actuators and operable during driving engagement of theactuators with their respective higher order wheels, for rotating insaid opposite direction the actuators so set for a primary transfer; anda plurality of gear despiraling means individual to said actuators andresponsive to movement of their respective actuators from said normalposition to said set position, each one of which despiraling meanseffects proper alignment of the register wheel with which its associatedactuator is engaged during a secondary transfer operation.

5. A simultaneously operable transfer mechanism for calculating machineregisters comprising; in each denominational order, a register piniongear and a transfer element rotatable therewith through a transferposition; a plurality of transfer actuators, one for each of said piniongears, said actuators each having a segment gear portion intermeshablewith the pinion gear of the next higher order and a pawl portionengageable with said transfer element of the pinion gear for which it isprovided as such transfer element rotates through transfer position;said actuators, during disengagement with their respective said higherorder pinion gears, being settable in a direction opposite to thedirection of rotation of said pinion gear by such engagement from anormal position to a set position for conditioning primary transferoperations; said actuators when in normal position and during engagementwith their respective said higher order pinion gears also being settableby such engagement from said normal to said set position simultaneouslywith said rotation of their associated said elements through transferposition to effect secondary transfer operations; said actuators beingfurthermore movable from said set position to a third position in saidopposite direction; and a driving bar com mon to said actuators andoperable, under conditions where said actuators are in engagement withtheir respective higher order pinion gears, for driving in said oppositedirection to said third position the actuators so set; and a pluralityof gear despiraling means, one for each of said actuators and responsiveto movement of its associated actuator from said normal position to saidset position for effecting proper alignment of the higher order piniongears with which such associated actuator is engaged during a secondarytransfer operation.

6. In a simultaneously operable transfer mechanism for calculatingmachine registers having, in each denominational order, an accumulatormechanism including at least one pinion gear adapted for rotativemovement for storing the input in its order and a transfer elementrotatable with said pinion gear through a predetermined transfer are; atransfer lever engageable throughout said are by said transfer elementand driven thereby; a transfer actuator engageable with the pinion gearof the next higher order, said actuator, during disengagement with saidhigher order pinion gear, being settable by driven movement of saidtransfer lever from a normal position to a set position in a certaindirection for conditioning a primary transfer operation; said actuatorbeing furthermore movable from said set position to a third position insaid certain direction; said actuator also having a portion which, whenthe actuator is in normal position and in engagement with said higherorder pinion gear, is engageable by said transfer element and, underconditions where said transfer element is rotated through saidpredetermined transfer arc, said portion drives the actuator into saidset position simultaneously with said rotation to effect a secondarytransfer operation; and a driving bar common to said actuators fordriving the actuators so conditioned for a primary transfer to theirrespective third positions during engagement with their respectivehigher order pinion gears and, in turn, simultaneously effectingsecondary transfers.

7. A transfer mechanism as set forth in claim 6 wherein latching meansindividual to said actuators are pro vided, said latching means beingresponsive to rotative movement of their respective associated actuatorsto said set position for establishing latching connections between saiddriving bar and the actuators conditioned for primary transfer erationsas the latter arrive at said set position.

8. In a simultaneously operable transfer mechanism for calculatingmachine registers having in each denominational order a register wheeland a transfer element rotatable therewith through a certain arcuatedistance in a first certain direction; a transfer actuator arranged fordriving engagement and disengagement with the wheel of the next higherorder; a transfer lever engageable by said element throughout saidarcuate distance, under conditions where said actuator is disengagedfrom its asso ciated wheel; said transfer lever being operable when soengaged to rotate said actuator through said certain arcuate distance ina direction opposite to said first certain direction from a normalposition to a set position for conditioning a primary transferoperation; said actuator being furthermore movable from said setposition to a third position in said opposite direction; said actuatoralso having a portion which, when the actuator is in normal position andin driving engagement with said higher order Wheel is engageable by saidtransfer element, said portion, under conditions where said transferelement is rotated through said certain arcuate distance, drives saidactuator into said set position simultaneously with said rotation toeffect a secondary transfer operation; and a transfer bar common to saidactuators, said transfer bar being operable, under conditions where saidactuators are in driving engagement with their respective higher orderwheels, for rotating in said opposite direction the actuators so set;and a plurality of gear despiraling means individual to said actuatorsand responsive to movement of their respect actuators from theirrespective said normal to said set positions for effecting properalignment of the register wheels with which their respective associatedactuators are in driving engagement during a secondary transferoperation.

9. In a simultaneously operable transfer mechanism for calculatingmachine registers having in each denominational order a register piniongear and a transfer element rotatable therewith through a transferposition in a first certain direction; a transfer lever rotatable bysaid element in a direction opposite to said first certain direction; atransfer actuator intermeshable with the pinion gear of the next higherorder, said actuator, during disengagement with said higher order piniongear, being settable in said opposite direction by said lever from anormal position to a set position for conditioning a primary transferoperation; said actuator being furthermore movable from said normalposition to a second position in said opposite direction; saidvactuator, when in normal position and during engagement with saidhigher order pinion gear, having a portion engageable by said element 18upon rotation through transfer position for moving the actuator intosaid second position simultaneously with said rotation to effect asecondary transfer operation; and a driving bar common to saidactuators, said driving bar being operable, under conditions Where saidactuators are in engagement with their respective higher order piniongears, for rotating in said opposite direction the actuators so set; anda plurality of gear despiraling means individual to said actuators andresponsive to movement of their respective actuators from said normalposition to said set position, each of said despiraling means effectingproper alignment of the register wheel with which its associatedactuator is engaged during a secondary transfer operation.

1-0. A transfer mechanism for a plurality of denominational orders forcalculating machine registers for simultaneously transmitting calculatedamounts between such orders for storage in accordance with predeterminedtransfer points between successive orders; said transfer mechanism ineach denominational order comprising; an accumulator mechanism includingat least one pinion gear rotatable predetermined amounts in proportionto the parts of its denominator to be registered for storing such partsinput; a transfer element rotatable with said pinion gear through acertain associated transfer position; a transfer actuator engageable indriving relation with the pinion gear provided for the next higher orderfor driving such next higher pinion; a transfer lever actuatable by saidtransfer element under conditions where said transfer element is rotatedthrough said certain transfer position during disengagement of saidactuator with said next higher order pinion gear; said transfer lever,when so actuated, actuating said actuator from a normal position to aset position in a certain direction for conditioning a primary transferoperation; said actuator being furthermore movable from said setposition to a third position in said certain direction; said actuatorhaving a portion which, when said actuator is in normal position and indriving engagement With said higher order pinion gear, is engageable bysaid transfer element; said actuator upon rotation of said transferelement through transfe' position being driven thereby to said setposition simultaneously with said rotation and driving its associatednext higher order pinion gear to effect a secondary transfer operation;a driving bar common to said actuators, said driving bar being operableduring engagement of said actuators with their respective higher orderpinion gears, for driving the actuators so conditioned for primarytransfers from their respective set positions to their respective thirdpositions, and, in turn, simultaneously effecting said secondarytransfers; and gear despiraling means, one for each of said actuatorsand operatively responsive to movement of its associated actuator fromsaid normal toward said set position for applying forces thereto aidingsuch movement.

11. In a simultaneously operable transfer mechanism for calculatingmachine registers having in each denominational order; a storagemechanism including at least one register pinion gear arranged forrotative movement predetermined discrete amounts in proportion tocertain corresponding inputs received by said machine; said registerpinion gear having a laterally extending member rotatable therewiththrough a predetermined transfer position for effecting a transfer ofthe accumulated input stored on the register gear to the storagemechanism provided for the next higher order; a longitudinal membermounted in position for actuation through a certain arcuate distance bysaid laterally extending member, under conditions where the latter isrotated through said transfer position; a segmental gear adapted forrotative engagement with the register gear of the next higher order andbeing conditioned from a first to a second position by actuation of saidlongitudinal member in preparation for a primary transfer operation,said segmental gear having a laterally extending lug engageable by saidlaterally extending member, upon rotation of said extending memberthrough said transfer position, for effecting a secondary transferoperation simultaneously with said rotation; a transfer bar common tosaid segmental gears and effective, under conditions where said registergears are in engagement with their respective segmental gears, forrotating the register gears so conditioned for a primary transfer acertain amount to effect said primary transfer and simultaneousiytherewith secondary transfers to the next, next higher order; and aplurality of spring means, one for each of said segmental gears andoperably connected thereto, said spring means being effective,uponrotation of the segmental gear for which it is provided from saidfirst toward said second position, for applying despiraling forcesthrough said segmental gears to their associated engaged register gearsto correctly align the register gears registering the secondarytransfers.

1 2. A transfer mechanism as set forth inrclaim 11 wherein saidsegmental gears are each provided with a transfer bar engaging side edgesurface including a transfer bar receiving cut-out portion definedtherein, and said transfer bar is yieldably mounted for limited radialmovement with respect to said segmental gears and spring biused againstsaid side edge surface for radial movement into said cut-out portionsestablishing individual latch ing connections between said transfer barand the saidv in each denominational order are formed integral one withthe other.

14. In a simultaneously operable transfer mechanism for calculatingmachine registers having, in each denomi-v national order; a storagemechanism including at least one register gear for accumulating certaininputs associated with its order, such register gear being arranged forrotative movement into a plurality of predetermined input storage,positions in accordance with the said associated inputs received by themachine, said register gear having a laterally extending memberrotatable therewith through a predetermined transfer arc for effectingtransfer of the accumulated input stored on the register gear to thestorage mechanism provided for the next higher order; a segmental gearadapted for inter meshing engage" ment with the register gear of thenext higher order; a longitudinal member pivotably mounted in positionfor constant driven engagement with said extending member underconditions where the latter is rotated through said transfer are andsaid segmental gear is disengaged from its associated register gear;said segmental gear being driven by said longitudinal member from afirst to a second position in preparation for a primary transferoperation, vsaid segmental gear having a laterally extending lugengageable by said extending member upon rotation through said transferare, under conditions where said segmental gear is intermeshed with itsassociated register gear, for effecting a secondary transfer operationsimultaneously with said rotation; a driving bar common to saidsegmental gears and effective, under conditions where said registergears are in engagement with their respective segmental gears, forrotating the prepared'register gears. insaid second position a certainamount to effect said primary transfers and simultaneously therewithsecondary transfers to the next, next higher order, and a plurality ofspring means, one for each of said segmental gears and operablyconnected thereto, said spring means being effective upon rotation ofthe segmental gear for which it is provided from said first to saidsecond position, for applying despiraling forces through said segmentalgears to their assoicated inter-meshed register gears to correctly alignthe register gears registering secondary transfers.

' 15. A transfer mechanism as set forth in claim 14 wherein saidsegmental gears are each provided with a driving bar engaging side edgesurface including a drivingbar receiving cut-out portion definedtherein, said driving bar is spring biased in a radial directiontowardsthe axis of rotation of said segmental gears for movement intosaid cut-out portions for locking thesaid segmental gears conditionedfor aprimary transfer operation to said driving bar asisuch conditionedgears arrive at said second position, and wherein said transfermechanism is provided effective after completion of said simultaneoustransfers for driving said segmental gears-back to said first position,said cam slot being configurated to cause actuation of said driving barout of said locking engagement with said segmental gears'as said drivingbar moves past said second position during segmental gear restoringoperation.

16. A transfer mechanism for a plurality of denominational orders forcalculating machine registers for simultaneously transmitting calculatedamounts between such orders for storage in accordance with predeterminedtransfer points between successive orders; said transfer mechanismcomprising; in each denominational order an accumulator mechanismincluding a pair of constantly inter-meshed pinion gears rotatablepredetermined amounts in proportion to the parts of the denominator oftheir order to be registered for storing such parts input; two transferelements, one for each pinion gear, rotatable with said pinion gearsthrough a certain associated trans for position; a transfer actuatorengageable in driving re-' lation with one pinion gear of the pairprovided for the next higher order for driving such next higher pair ofpinion gears; a transfer lever actuatable by the transfer? element oftheopopsed gear of the pair associated with its order-under conditionswhere such transfer element is rotated through said certain transferposition during disengagement of said actuator with said one next higherorder pinion gear; saidtransfer lever,- when so actuated, actuating saidactuator from a normal position to a set position in a certain directionfor conditioning a primary transfer operation; said actuator beingfurthermore movable from said set position to a third position in saidcertain direction; said actuator having a portion which, when saidactuator is in normal position and in driving engagement with said onehigher order pinion gear, is engageable by the transfer element opopsedto the transfer ele-. m-ent operating said lever; said actuator uponrotation of said opopsed transfer element through transfer positionbeing driven thereby to said set position simultaneously with saidrotation and driving its associated said one next higher order piniongear to effect a secondary transfer operation; a driving bar common tosaid actuators, said driving bar being operable during engagement ofsaid actuators with their respective said one next higher order piniongears, for driving the actuators so conditioned for primary transfersfro-m their respective set positions 4 to'their respective thirdpositions, and, in turn,v simultaneously effecting said secondarytransfers; and gear despiraling means, one for each of said actuatorsand operatively responsive to movement of its associated actuator fromsaid normal toward said set position for applying forces thereto aidingsuch movement.

17. A simultaneously operable transfer mechanism for calculating machineregisters comprising; in each denominational order, a register piniongear and an associated transfer element rotatable therewith through atransfer position, saidregister pinion gear and associated transferelement being rotatable in unison in a first direction for additiveregister operations and in a second direction opposite thereto forsubtractive register operations; a transfer actuator having a segmentgear portion inter-V Imeshable with the pinion gear of the next higherorderv and a pawl portion engageable with said associated trans:

fer element under conditions Where such transfer element rotates throughtransfer position; said actuator, during disengagement with'itsrespective said higher order pinion gear being settable by such transferelement engagement from a normal position to a set position in adirection opposite to the direction of rotation of such associatedtransfer element to condition additive and subtractive primary transferoperations; said conditioned actuator being further movable from saidset position to a third position in said direction opposite to thedirection of rotation of such associated transfer element; said actuatorwhen in normal position and during engagement with said higher orderpinion gear also being settable by such transfer element engagement fromsaid normal to said set position in a direction opposite to thedirection of rotation of such associated transfer element to effectadditive and subtractive secondary transfer operations; a pair ofdriving bars common to said actuators and operable in opposite rotativedirections one to the other, said oars, under conditions where saidactuators are in engagement with their respective higher order piniongears, being effective for driving said conditioned actuators from saidset position to said third position efiecting additive and subtractiveprimary and secondary transfers.

18. A simultaneously operable transfer mechanism for calculating machineregisters comprising; in each denominational order, a register piniongear and an associated transfer element rotatable therewith through atransfer position, said register pinion gear and associated transferelement being rotatable in unison in a first direction for additiveregister operations and in a second direction opposite thereto forsubtractive register operations; a transfer actuator having a segmentgear portion intermeshable with the pinion gear of the next higher orderand a pawl portion engagea-ble with said associated transfer elementunder conditions where such transfer element rotates through transferposition; said actuator, during disengagement with its respective saidhigher order pinion gear being settable by such transfer elementengagement from a normal position to a set position in a directionopposite to the direction of rotation of such associated transferelement to condition additive and subtractive primary transferoperations; said conditioned actuator being further movable from saidset position to a third position in said direction opposite to thedirection of rotation of such associated transfer element; said actuatorwhen in normal position and during engagement with said higher orderpinion gear also being settable by such transfer element engagement fromsaid normal to said set position in a direction opposite to thedirection of rotation of such associated transfer element to effectadditive and subtractive secondary transfer operations; a pair ofdriving bars common to said actuators, one of said bars for additivetransfers and the other for subtractive transfers, said bars beingoperable, under conditions where said actuators are in engagement withtheir respective higher order pinion gears, said one bar for drivingactuators conditioned for additive transfer from said set position tosaid third position, in a direction opposite to said first direction,and said other bar for driving actuators conditioned for subtractivetransfer from said set position to said third position in a directionopposite to said second direction, and gear despiraling means, one foreach of said actuators and responsive to movement of its associatedactuator from said normal to said set position during additive andsubtractive secondary transfer operations for effecting proper alignmentof the higher order pinion gear then engaged with said associatedactuator, said gear despiraling means being selectively conditionble foreffecting such proper alignment during additive and subtractivetransfers.

Horton Nov. 11, 1930 Reynolds Nov. 16, 1954

1. IN A SIMULTANEOUSLY OPERABLE TRANSFER MECHANISM FOR CALCULATINGMACHINE REGISTERS HAVING IN EACH DENOMINATIONAL ORDER A REGISTER WHEELAND A TRANSFER ELEMENT ROTATABLE THEREWITH THROUGH A TRANSFER POSITION;A TRANSFER ACTUATOR ARRANGED FOR DRIVING ENGAGEMENT WITH THE WHEEL OFTHE NEXT HIGHER ORDER AND HAVING AN INTEGRAL PORTION EXTENDING INTOPOSITION FOR ROTATION OF SAID ACTUATOR BY SAID TRANSFER ELEMENT IN ADIRECTION OPPOSITE TO THE DIRECTION OF ROTATION OF SAID REGISTER WHEELUNDER CONDITIONS WHERE SAID TRANSFER ELEMENT IS ROTATED THROUGH SAIDTRANSFER POSITION, SAID TRANSFER ELEMENT ROTATING SAID ACTUATOR IN SAIDOPPOSITE DIRECTION FROM A NORMAL POSITION TO A SECOND POSITION; SAIDACTUATOR BEING FURTHERMORE MOVABLE IN SAID OPPOSITE DIRECTION FROM SAIDSECOND POSITION TO THIRD POSITION; A DRIVING BAR COMMON TO SAIDACTUATORS AND OPERABLE, DURING DRIVING ENGAGEMENT OF SAID ACTUATORS WITHTHEIR RESPECTIVE HIGHER ORDER WHEELS, FOR ROTATING THE